Machine tool spindle and variablespeed drive therefor



May 20, 1952 T. F. ESERKALN 29597,?16

MACHINE TOOL SPINDLE AND VARIABLE-SPEED DRIVE THEREFOR Filed March 30, 1948 3 Sheets-Sheet l May 20 1952 T. F. ESERKALN 2,597,716

MACHINE TooL SPINDLE AND VARIABLE-SPEED DRIVE: THEREFOR Filed Maron 30, 1948 5 sheets-sheet 2 7/ INVENTOR.

May 20, 1952 T. F. ESERKALN MACHINE TOOL SPINDLE AND VARIABLE-SPEED DRIVE THEREFOR 5 Sheeics-Sheet 5 Filed March 50, 1948 Patented May 20, 1952 MACHINE TOOL SPINDLE AND VARIABLE- SPEED DRIVE THEREFOR Theodore F. Eserkaln, Wauwatosa, Wis., assignor to George Gorton Machine Co., Racine, Wis., a

corporation of Wisconsin Application March 30, 1948, Serial No. 17,837

4 Claims.

1 The invention relates particularly to rotary spindles such as the so-called cutter spindles of milling machines and the like machine tools, and to a selectively variable change speed drive transmission therefor; and the nature and objects of the invention will be readily understood by those skilled in the arts involved in the light of the following explanation and detailed description of the accompanying drawings illustrating what I now believe to be the preferred embodiments or mechanical expressions of my invention from among various other forms, expressions, embodiments, arrangements, `modifications, designs. constructions and combinations, of which the invention is capable within the spirit and scope thereof as'deiined by the hereinafter appended claims. y

The primary problems with which my invention is concerned are those particularly encountered in providing for milling or the like machine tools of the relatively `high powered, heavy duty types having a horizontally disposed cutter spindle, a variable or change speed drive of the gear type for driving the cutter spindle, in which the over-all range of speeds through which theA spindle may be driven are obtained through selectively operable basic speed ranges and a speed 'change mechanism operatively common to all the speed ranges for varying the speed at which the cutter spindle may be driven through any one of the basic speed ranges selected for operation.

And a general object of the invention is to provide a design and arrangement for such a change speed spindle drive by which the number of basic speed ranges may be increased to thus increase the over-all speed range over which the cutter spindle may be driven, without mechanical or gearing complications and while maintaining compactness with simplicity of structure and high operating efficiency, so that such drive mechanism may be associated in efficient driving relation with a cutter spindle and may be located and efficiently mounted in a minimum of space within the basic frame or column structure provided by a horizontal spindle type of machine tool without requiring increase in `the size or dimensions of such basic structure.

A further object is to provide a'simplied gear train system for such a cutter spindle drive in whichthe number of shift controls necessary to effect speed changes throughout the over-all speed range of which the drive is capable, is reduced to a minimum. y

Another object is to provide an arrangement of simple compound gear train units in the spindle drive and to so arrange such units that the secondary or driven gears of each unit attain maximum diameters and form a relatively large diameter weight mass for developing a substantial fly wheel effect acting on the shaft or spindle on which such driven gears are mounted.

Another object is to provide an arrangement of such a cutter spindle drive in which two shafts only are required between the power input point to the drive and the cutter spindle.

Another object of the invention is to reduce lateral deflection and torsional deflection on the driving and driven shafts associated with the gear trains.

Another object is to provide a change speed gear drive from a motor to a machine tool cutter spindle in which all the shafts associated with the gear trains of the drive between the motor shaft and the spindle are parallel to each other and to the axis of the motor shaft in order to eliminate any angle drives between the motor and the cutter spindle.

And a further object is to provide a design of a dual directional cutter spindle drive by which the axis of the cutter spindle and the axes of all the shafts associated with the gear trains of the drive between the motor and the spindle are located in the same plane in order to assure a minimum load on the shaft bearings and thus reduce to a minimum the possibility of cramping action when the drive is operated to rotate the spindle in one of its directions of rotation.

Another object is to provide a design and arrangement of such a drive in which at least three (3) basic speed ranges may be provided with a single change speed unit operative to effect speed changes over any selected one of the three (3) basic speed ranges.

Another object is to provide such a spindle drive having at least three (3) basic speed ranges deiined by sets of pairs of range gears in which one of the range gears of each set is directly mounted on and carried by the cutter spindle, so that, the cutter spindle itself thus directly mounts and carries at least three (3) range gears.

A further object is to provide a cutter spindle having at least three (3) range gears directly mounted thereon in which such gears are so located on the spindle as to apply the transmitted torque from any one of said gears to the spindle at a location on the spindle in close proximity to the front bearing therefor immediately adjacent the operating end or nose of the spindle.

Another object is to design the range gears so mounted directly on a cutter spindle, in such a manner that the gears will provide a substantial weight mass to develop for the spindle an eiective ily-wheel effect acting in close proximity to the nose of the spindle.

Another object is to provide at least three (3) range gears directly mounted on a cutter spindle for selective operation to drive such spindle, and to so design, arrange and mount such gears that the gear spaced at the greatest distance inwardly on the spindle from the spindle nose will apply its torque to the spindle at a location spaced from the gear outwardly along the spindle toward and in close proximity to the operating end or nose of the spindle.

A further object is to provide a design and arrangement of a spindle drive that includes a change speed mechanism of the gear train type and a series of sets of pairs of range gears for selective operative association with the change speed mechanism, in which only two (2) active gear contacts dened by the engagement of two (2) gears of the change speed mechanism and by the engagement of the two (2) gears constituting the pair of range gears of the selected range, respectively, are required to be engaged and set up for driving the spindle for any speed setting of the speed change mechanism in any selected speed range, to thus decrease wear and maintenance and increase operating eciency.

With the foregoing general objects, features and results as well as certain others in View, which others will be readily apparent from the following detailed description and explanation, my invention consists in certain novel features in design and construction of parts and elements and in combinations and arrangements thereof, all as will be more fully referred to and described hereinafter.

Referring to the accompanying drawings in which similar reference characters refer to corersponding parts and elements throughout the several figures thereof Fig. 1 is a view in side elevation of a milling machine of the horizontal spindle type embodying a horizontal cutter spindle and drive therefor of my invention, the cutter spindle and range gears mounted thereon being shown in dotted lines.

Fig. 2 is a view in side elevation of the spindle unit including the horizontal spindle and the range gears directly mounted thereon at the operating end or nose of the spindle.

Fig. 3 Ais a view in vertical section through the upper portion of the column of the milling machine of Fig. 1, showing the horizontal spindle and spindle drive transmission, including the sets of range gears and the change speed gear unit, and also showing a portion of the motor driven belt and pulley power transmission to the spindle drive.

Fig. 4 is a perspective view of the horizontal cutter spindle, and the change speed spindle drive, including the sets of range gears and change speed gearing unit with the manually controlled selector mechanism therefor, all of the elements being separated or pulled apart but maintained in their general positions relative to each other.

An application of a horizontal cutter spindle and a change speed drive therefor of the invention to a milling machine of a relatively high powered, heavy duty, knee and column type, is illustrated in the accompanying drawings to serve as an example for purposes of explaining the principles and features .of the invention. But, it

is to be here noted that the expression and embodiment of a cutter spindle and drive here shown is primarily by way of example and not in all respects of limitation, as the invention is not restricted to application to the particular type of horizontal spindle column and knee milling machine of the illustrated example, and further, various features of the cutter spindle and drive are adapted for application to machine tool spindles generally.

The milling machine of the example, referring to Fig. l, embodies the main frame structure in the form of a vertical column I having mounted at the forward side thereof the vertically movable y knee II, on which is mounted the saddle I2 for transverse or in and out movements on the knee relative to the machine, and the work table Id mounted on the saddle for movements longitudinally of the machine along a path perpendicular to the path of movements of the saddle I2. Such column, knee, saddle and work table arrangement may be considered to be more or lessconventional for purposes of this example, and to include any usual power and/or manual operating mechanism for effecting movements of such elements.

The column structure I9 at the upper end thereof is, in this particular form of horizontal spindle type of milling machine, provided with a horizontally disposed head or ram I5 adjustably slidably mounted thereon with the forward length of the ram projected to extend over and above the work table Id therebelow, as will be understood by those familiar with this general type of milling machine.

A spindle 29, referring now to Fig. 3 in particular, for driving any suitable rotary tool such as a milling cutter, is mounted in the upper end portion of column structure I0 below the ram I5, in horizontall position extending through the column from front to rear of the machine, with the forward operating end or nose 2I located in and accessible through the forward wall Illa of column I0 above work table I4. Spindle 20 is mounted and journalled at its forward end in an annular, roller bearing assembly 20a of the combined radial and thrust type, with this bearing mounted in the forward wall IIla immediately adjacent the rear or inner side of the spindle nose 2|. The rear end of spindle 20 extends through the rear vertical wall Ib of column structure I0 and mounts and is journaled in a suitable annular roller bearing assembly 2Gb of the radial type which is positioned and mounted in such rear wall Ib. An annular, roller bearing assembly 2te of the combined radial and thrust type is mounted in a vertically disposed transverse wall or partition Ita within and forming a portion of column structure IIJ, at a location spaced a distance inwardly of spindle 2i) from the forward end bearing 26a, and this bearing assembly 20c so mounted, receives and journals therein the spindle 20, as will be clear by reference to Fig. 3 of the drawings. Bearing assemblies 20a and 20c are mounted and arranged relative to the spindle 20 to care for thrust forces acting along the spindle in opposite directions axially thereof.

The cutter spindle 28 may be of the usual type having an axial bore therethrough from end to end thereof, in which there is ,mounted adraw bar 20d extending therethrough for adjustment from the rear end thereof to releasably secure a cutting tool or arbor in mounted position in the spindle nose 2I, as willk be readily understood by those skilled in this art.

MP in turn drives a pulley SP which is mounted in position on column l0 above pulley MP through amultiple V,belt system B connecting these two pulleys in driving relation. The belt drive transmission comprising pulleys MP and SP with the belt system B, may, as in the example hereof, be mounted and positioned at the exterior of the rear wall Hlb'of column structure I0 and be enclosed in a suitable removable casing l1 (see Figs. l and 3). The motor M is preferably of the reversible type so that the spindle drive of the invention may be operated to rotate the spindle 'in either direction. Obviously, if found desirable or expedient, other means for operating the drive to rotate the spindle in either direction could be employed, such for example, as the interposition of a suitable reversing gear or the like unit (not shown) between the motor and the spindle drive organization. f

Pulley SP is mounted on the rear end of a drive shaft 22. This drive shaft 22 is mounted in the column l0 in horizontal position spaced below cutter spindle 20. Shaft 22 is mounted in position parallel with the cutter spindle 20 and is located relative to the spindle so that its axis of rotation is disposed in the vertical plane passing through the spindle axis of rotation. The drive shaft 22 is journaled at the forward and rear ends thereof in roller bearing assemblies 22a and 22h respectively. The forward inner end of drive shaft 22 is connected by a suitable coupling unit 22a into driving relation with the rear end of the horizontally disposed power input or driving shaft 23 of a change speed gear mechanism or unit CS, through and from which unit the spindle 20 may be driven at a selected speed within the speed range of the unit and associated drive between that unit and the spindle. Power input shaft 23 of unit CS is mounted in axial continuationV of drive shaft 22 and hence, is disposed parallel with cutter spindle 20 with its axis of rotation in the vertical plane passing through the axis of rotation of the spindle.

A counter shaft 24 is mounted in horizontal position within the column structure I0, between and parallel with driving shaft 23 of the change speed .gear unit CS and the cutter spindle 20 thereabove. Counter shaft 24 so mounted is located relative to shaft 23 and the cutter spindle 20, so that its axis of rotation lies in the vertical plane which passes through the axes of rotation of shaft 23 and spindle 20. The counter shaft 24 extends through and across the column structure I0 and is mounted and rotatably journaled at its forward end in the hollow hub 26h, of the relatively large diameter, high speed range gear H. Gear H is rotatably mounted and journaled by a forward extension of the hub 26h thereof, in an annular roller bearing assembly 24a mounted in the forward wall |011 of the column structure l0. Such mounting of the forward end of counter shaft 24 provides for rotation of the high speed range gear H and the counter shaft independently of each other about the common axis providedrby the shaft. The rear end of counter shaft-.p24 is mounted and rotatably journaled in an annular roller bearing assembly 24o mounted in fixed structure within the column l0 supported from the rear wall Illh thereof. The counter shaft thus extends through and across column l0 from the forward wall lila to the rear wall 10b thereof, above driving shaft 23 of change speed gear unit CS, and that 1ength or section of counter shaft 24 which is opposite and above driving shaft 23, provides the driven shaft 25. A bearing 24e is provided for the counter shaft 24 intermediate the length of the shaft and, in this instance, such bearing is constituted by an annular roller bearing assembly mounted in fixed structure provided by column I0 and being located at the forward end of driving shaft section 25 of the counter shaft above the forward end bearing 23o for the driving shaft 23 of unit CS. The portion or section of the counter shaft 24 which 'extends from the forward end'of driven shaft section 25 in the bearing 24e to the high speed range gear H, provides a power take-off shaft section 26 from which power is transmitted to the cutter spindle 20 through the range gears to be hereinafter described.

The cutter spindle drive is, in this instance, of the dual directional type, that is, it may be operated to rotate the cutter spindle 20 in either direction. By the mounting and arrangement of the spindle 20, counter shaft 24 and driving shaft 22-23 in parallelism with their axes of rotation and the axes of their supporting bearings disposed in the same vertical plane, the possibility of any cramping effect or pinch bar action being developed when the shafts of the drive are operated for rotating spindle 20 in one of its directions of rotation, is reduced to a minimum.

The power take-off shaft section 26 of the counter shaft 24 is formed with a series of splines 26a thereon between the change speed gear unit CS and the high speed range gear H at the forward end of the shaft. A gear cluster or couplet unit 29 comprising the low speed range gear L and the intermediate speed range gear I, is mounted on and splined to power take-olf shaft 26 in position with the intermediate range gear I thereof located on the shaft between the high speed range gear H and the low speed range gear L. Low speed range gear L is in the form of a relatively small diameter pinion gear, ywhile intermediate speed range gear I is of a diameter greater than the diameter of gear L but less than the diameter of the high speed range gear H. This gear cluster 29 is slidable as a unit on the take-off shaft section 26 between a position with the intermediate range gear I adjacent and in engaged driving relation with the h igh speed range gear H, and a position with the low speed range gear L located at the rear end of shaft section 2E adjacent to change speed gear unit CS and with the intermediate range gear I moved rearwardly on the shaft to a position disengaged from the high speed range gear H.

The high speed range gear H at the inner side thereof is provided with an annular series of clutch teeth 21 therearound projecting rearwardly therefrom concentric with the axis of the gear, and the intermediate range gear I is provided at the outer side thereof facing gear H with an annular series of clutch teeth 28 positioned thereon and therearound for clutching engagement with the teeth 21 of the high speed range gear H when the gear cluster unit 29 is moved forwardly on shaft section 26 to position range gear I for engaging the clutch teeth 28 thereof with the clutch teeth 21 of gear H. Thus, in the engaged position of 'the high speed range .gear Hlwith the intermediate speed range :gear I of the 'slidable gear 4cluster unit 29, the high speed rangegear H will bedrivenby and from the shaft section .26 and the intermediate range .gear I. Thegear vcluster unit 25 is provided Awith an annular groove 29a therearound between Arange gears I and L thereof, for slidably receiving a suitableshifting forkfor selectively shifting the gearcluster unit to 'and'betweenits several .operative positions lon shaft section 2t, as will be =explained hereinafter.

`In accordance with an important feature of my invention, the cutter spindle '2t directly mounts thereon aseries-of at least three (3) speed range gears, namely, a 'high speed range gear SH of the helicalorspiral type, an intermediate speed'range gearSL-and a lowspeed range or socalled bull gearSL, gearsSI `and SL Vin this -instance Ibeing of the spur type. The high speed range .gear SH on spindle 26 is of considerably smaller diameter than, and is Vadapted to be selectively engaged by, the high speed range gear H on shaft section 26, range gear H beingof the helical or spiral type for operative meshing with gearaSH. kThe gears .I-I and SH thus form a set or pair 4of gears for drivingspindle 2t from counter shaft .24 lin the high speed range. Intermediate range gearSI on spindle 20 is of greater diameter than '.the diameter of gear SH, and is adapted to be engaged by the intermediate range gear I of the :gear cluster unit 29 on shaft section 2d. Intermediate range gear SI is in this instance of greater diameter than the diameter of gear I to .abe engaged therewith. The spindle mounted gear SIzand-thegear I on shaft 28 thus provide the set or pair of gears for driving spindle 20 from counter 'shaft 2'4 in the intermediate speed range, while low speed range gear SL on spindle 20 .isadapted to be selectively engaged with the range gear L on the movable gear cluster unit on shaft 'section v25 to thus provide a set or pair of gearsfor driving spindle 20 from counter shaft 24 kin the .low speed range of operations of the spindle.

YThe helical or spiral, relatively small diameter high speed rangegear SH of the spindle mounted range gears, Vis located on and Vkeyed to the spindle .2G at the inner end of the spindle nose 2| immediately adjacent the inner side of the forward wall lila of the machine column structure 1.0, this range gear SH Vbeing of general pinion form.

The spindle mounted intermediate speed range gear SI .has a relatively greater diameter than the diameter of the .pinion gear SH, and is of .subs'tantial thickness to provide a large diameter, solid `material hub portion-h, the diameter of which .is =but slightly less than the operating, tocthed vportion'proper of the gear. Gear .SI is keyed on spindle 2t with the forward side thereof abutting the adjacent rear side of range gear SH and with the gear forming toothed portion thereof adjacent gear SH, so that the hub portion h thereof is disposed at `the inner side of the gear opposite the forwardly mounted gear SH. Spindle mounted intermediate range gear SI, so constructed, thus provides a relatively heavy, large diameter weight mass immediately adjacent the forwardly mounted range gear SH at the operating end or nose 2| of the spindle 2G.

'The spindle mounted, low speed range gear SL, the so-called bull gear, is of greater diameter than the diameter of the intermediate range gear SI, and is formed of substantial thickness to provide 'a large diameter, solid material hu'b portion 'h' :of .considerable .thickness or width relative -to .the toothed -portion of the gear with the rearward portion h" thereof formed of a diameter substantially equal .to the 'diameter of hub hof the range .gear SI. Hub h of .gear SL may be sloped or inclined radially `outwardly from 'the .portion h'" thereof toa .location around and adjacent the'inner side of 'the toothed -por-- tionof the gear. By'this design'and/construction, the spindle mounted 'low speed range vgear "SL provides a .relatively heavy, large diameter weight mass on the spindle 2li Vadjacent 'the Ynose 2| of the spindle.

The spindle mountedrelativelysmall diameter, helical high speedrange gear SH is of substantial width and, in this example, is toothed vcompletely across its width. This gear SH .also has substantial depth or thickness and .is formed vto provide a solid material hub portion h" which, in this instance, extends through lthe full width of the gear (see Fig. 3). Thus, Ithe high speed range gearSH presents a Vrelatively heavyweight mass.

The high speed rang gear SH .is vmounted on the spindle in immediate proximity Aand juxtaposition tothe spindle nose 2l. The intermediate speed range gear SI is mounted on the spindle immediately adjacent and juxtaposed lto high speed gear SH. The large diameter low speed range gear SL is mounted on the spindle 2!) immediately adjacent and in juxtaposition 'to the intermediate range gear SL, -so that the forward side of gear SL is substantially against and abuts the facing inner side of the adjacent intermediate speed range gear SI. Hence the relatively large Weight masses provided by the gearsSI-IfSI, and SL with their hubs h, h' and h'", respectively, are combined intowhat in effect is-a'single structure of relatively large diameter -providing a single weight mass or fly-wheel adjacent and in immediate proximity to the nose 2| of the spindle.

In accordance with a further 'feature -of -my invention, the large diameter, `low speed range gear SL with its high weight mass is mounted on the spindle 2] relative to Vthe intermediate range gear SI -in such a mannerthat the torque transmitted by gear SL to the spindle will be applied at a locationspaced forwardly along the spindle and in relatively close proximity to the operating end or nose 2| from the location on the range gear SL at which gear SL Areceives the torque from the low speed range gear L on the shaft section 26 when the gears L and 4SL are in operative driving engagement.

lIn the present example, such result is obtained Aby mounting the low speed'range gear SL on the spindle 2li immediately adjacent the inner side of the intermediate speed range gear SI with the forward side of gear SL substantially against or abutting the facing inner side of .the adjacent gear SI. The relatively vlarge diameter, low speed range gear SL in accordance with 4this feature of my invention, is notdirectly connected to the spindle but is directly connected t0 the adjacent intermediate .range .gear SI by keying, or otherwise suitably connecting the 'hub portion h of gear SL .to the adjacent hub portion h of the gear SI. For instance, diametrically opposite, radially disposed ikeys 1c may be formed on hub portion h" of gear SL and seated `and secured .in facing ,keyways or slots formed in the adjacent abutting surface of the hub ,portionJL transmitted to the intermediate range gear SI at a location spaced forwardly along spindle 26 from the plane of the toothed portion of gear SL to which the driving torque is applied from the range gear L on shaft section 26. Hence, the torque from range gear SL is applied to the spindle 20 at a location substantially closer to the operating end or nose 2| of the spindle, than the location on spindle 26 at which torque is transmitted to gear SL from gear L.

The three (3) range gears SL, SI and SH are directly mounted on the horizontal spindle 29 immediately adjacent and in proximity to the nose 2| of the spindle and the front bearing 26a therefor, with the gear SH at the inner side of bearing 29a immediately adjacent thereto, gear SI immediately adjacent and in effect abutting gear SH at the inner side thereof, and the gear SLimmediately adjacent, abutting and directly connected to the inner side of gear SI. By providing `each of the intermediate and low speed solid material hubs h and h', respectively, and the relatively Wide helical high speed range gear with the Wide solid material hub h", these gears together provide a substantial weight mass which is located in close proximity to the nose 2| of and the forward bearing 20a for, the spindle 2l! with the result that a very effective flywheel effect is developed acting at the operating Vrend of the spindle in close proximity to the spindle nose 2|.

Helical range gear H on shaft section 26 is mounted on the forward end of that shaft for rotation on and independently of the shaft and is in constant mesh with the helical range gear SH which is mounted directly on and keyed to the spindle 20 for rotation with the spindle. These constantlyV engaged gears H and SH comprise the set of gears for rotation of spindle 29 in the high speed range. The gear cluster 29 Which-includes range gear I is splined to and slidable axially of shaft section 26, and range gear I is adapted to be engaged with range gear SI directly mounted on spindle 2|] to provide the set of range gears for driving the spindle 20 in the intermediate speed range. Range gear L of gear cluster 29 is adapted to be engaged with the low speed range or bull gear SL mounted on spindle 20 and connected into driving relation therewith through the spindle mounted gear SI. Range gears L and SL provide the set of gears for driving spindle 29 in the low speed range.

The gear cluster unit 29 slidably mounted on shaft 2E is so designed that when it is moved axially inwardly on the shaft to position engaging range gear L thereof with the spindle mounted range gear SL, range gear I is disengaged from spindle mounted range gear SI, as well as being out of engagement with high speed range gear H on the shaft section 26. The spindle 2B will then be driven from shaft section 26 through the engaged range gears L and SL, in the low speed range.

Attention is here directed to the fact that the spindle mounted low speed range gear or so called bull gear SL is mounted and positioned on the spindle as the inner or rearmost gear of the series of spindle mounted range gears, and that the low speed range gear or so called bull pinion L, of the shiftable gear cluster 29 on the power take-off shaft 26, is when moved inwardly of that shaft to position engaged with the spindle mounted bull gear SL, located in immediate proximity to the bearing 24e of the counter-shaft 24 which is located at the inner end of shaft section 26. This arrangement substantially elimi- 10 nates or reduces to a minimum any lateral deflection of the shaft 26 as Well as reducing to a minimum 4any torsional deflection of this shaft under the loads imposed thereon with the low speed range gears L and SL in engagement for driving the spindle 29 from shaft 26.

When gear cluster unit 29 is moved axially forwardly on shaft section 26 to a position engaging range gear I thereof with the spindle mounted range gear SI, then gear L of unit 29 is in position disengaged from the spindle mounted range gear SL while the clutch teeth 28 of the gear I remain in position out of engagement with the clutch teeth 2l of high speed range gear H. When gear cluster unit 29 is moved axially in a forward direction on shaft section 26 4into a position with the clutch teeth 28 on range gear I engaged with clutch teeth 2'|`of the high speed range gear H to placethe latter in driving connection with shaft 26, then the range gearsI and L of unit 29 are disengaged from the spindle mounted range gears SI and SL, respectively. Except when engagedin driving. connection with gear I of unit 29, the high speed range gear H on shaft section 26 is idly rotated on and independently of shaft section 26 by the rotation of the spindle mounted-range gear SH with which range gear H is in constant mesh.

A manually operable speed range selector control is provided for actuating the range gear cluster unit 29 on shaft section 26 to selectively set up any desired one of the three (3) sets of y range gears L and SL, I and SI, or H and SH, respectively, so that the cutter spindle 20 will be driven from. shaft section 26 in the selected speed range.r Any suitable ordesired mechanical arrangement for effectingv selective setting up into operative position, of any one of the three sets of range gears may be provided. In the present example, I happen to show such a control which embodies a hand crank 39, referring now to Figs. 1 and 4, located yat one side of the column structure I6 on the` exterior thereof at the upper side of the outer face or dial mounting plate D of the change speed unit CS on which the manual control for such change speed unit is also mounted.

A range selector control mechanism for operation by such hand crank 39, is more or less schematically illustrated in Fig. 4 primarily to generally indicate a possible form of such a mechanism by which the slidable gear cluster unit 29 may be selectively actuated to position for setting up the range gears for operation of spindle 2l) in a desired speed range. For instance, the hand crank 30 may be mounted on the outer end of a generally horizontally disposed shaft 30a extending into column structure I0. Shaft 30d. is suitably mounted and journaled for rotation in either direction by hand crank 30 and at the inner end thereof is provided with a crank arm 30d. A slide member 3| may be slidably mounted on a rod or guide Bla fixed in horizontally disposed position parallel with and in the general horizontal plane of counter shaft 24. The rod or guide 3| a and slide 3| mounted thereon are positioned forwardly and generally opposite and along the section 26 of counter shaft 2li on which the range gear cluster 29 is slidably mounted. A shifter fork 32 is mounted in xed position on slide 3| for movement with the slide as a unit, and extends inwardly from one end thereof to the range gear cluster unit 29 with the inner forked end 32a of fork member 32 slidably received and engaged in the annular forky groove 29a ofY gear atom-.ie

cluster unit 29 (see. Fig. 3). Thus, movements of: slide 3| in either,` direction-along guide 3la ina straight line parallel with the. axis of shaft section 26 will slide gear-cluster` 23; on shaft section 26 in a corresponding direction. Suitable operating connections are providedll'between the cra-nk arm 36d and# the Aadjacent en d ofslide 3 l, suchiconnections including in the eszample here.- of; airoller 30e on crank arinlSUd engaged in a verticallyvdisposed groove 36d in the slide- 3l, as generally indicated in Fig. 4.

In thisv instance, rotation of the range. speed selector-hand crank 30 to the right or clockwise will move slide 3| andfork 32 to the right to slide gear clusterunit 29 outwardlyalong shaft section; 26 until the clutch teeth 28r ofy the intermediate. range gearv I are` engaged` withv clutch teeth 2-1 of thehigh speedrange gear H, thus engaging these gears in driving relation sothat high speed range gearA His-.then-.driven by shaft section 26 and drives the spindle mounted high speed range gear SHvwith which it is in constant meshY to therebydrive cutter spindley 20 inthe high speed range.

Hand crank 36- is swung to its limit of movement to the left or counter clockwiseY in order to set upthe low speed range gears L and SL for driving spindle 20 from shaft section 26. in the low speed range. In such low speed range selectionV posi-tion of hand-crank 36., the slidev3l is moved thereby-to thev left to position in which shifter fork 32 hasmovedgea-r cluster 29 on shaft 26-to-` position with the low-speedrange gear- L of; the cluster unit engaged with the spindle mounted low speed range gea-r- SL.

Theintermediate speed` range selection position of'the handcrank--S is; at a locationintermediate the extreme positions` thereof swung to the right for high speed range selection and swung to,theleftfor low speed'range selection, respectively, as referred to hereinabove.

Ero'meither-high or low speed range selection position, h and cranklBG is swingto an intermediate position such thatl slide 3| and its fork member 32 will have movedgear cluster unit 29 to a position in which the intermediate range gear I of the cluster unit will beengaged with the spindle mounted intermediaterangegear-.SL In this position, spindle 26 will bedriven iii-the intermediate speed range from the shaftl section 26'.

The arrangement of the range gear cluster29 on shait section 26v relative to the-high speed rangegear Hon that shaft section and to the range gears SL andSI mounted directly on the spindle 2); is such that gear unit 29 in shifting between high, intermediate, and low speed range selection positions, passes through aneutral positionnwiththegearsnof-all three (3) sets of range gears disengaged; and inactive. Innthe normal operation of the sets otrangegears, this neutral position is a transient one. However, if for some reason the operator should desire toA turn the cutter spindle vby hand, he could do so by shiftine gear, Chisterv 2,9 to. and leevieeitin suehneu-V irel position This ieeriria1-lyv transient neutral position in'H whichpthe cutter spindle 20` is completely disengaged fromdriving connection with Counter Shaft@ endrsheft section 2S tifiereof,v is shownin Eig, 3 ofgthedrawings Thej face` or` dial plate D of4 the change speed unit CSV may be provided with suitable markings indicating` the low, intermediatey and high speedrange selection positions of the hand crank 30 thereon.

The change speed,gear.unitf CS isA interposed-:in

driving association between themotor driven orv power. shaft 2l.v and the counter shaft. 24 for transmittingedrivingpoweravv from the shaft 2,2through a selectedspeed step of unit CS andaselected set ofthe range gears, tothev cutter spindle 2.6. In this example, this. change speed gear unit CS includesthe. driving` shaft 2,3i which isi-mounted and'journaled-.atlits' opposite ends.A in the bearing assemblies 23a andA 2.31), mounted intheA spaced bolsters or bearing supports, 23e and 23d, respectively, extending inwardly from the inner side ofthe face plate D of the unit. Driv-ingshaft 23 is axially alignedwith power shaft 22.' and is connected inv driving relation with shaft 22 by the shaft coupling 22c.

The driving shafty 23 is formed with aseries of splines `23e thereon andmounts. af series of'three (3) primary gear` couplets 46; 5D andll; each-of which is splned .to 4the shaft and-tis independently slidable` axially thereon in either direction. Gear coupletllleis positioned on shaft 23 adjacent that endof the shaftcoupled'with drive shaft 22, that is the-left hand end when facing Figs. 3 and 4, and includes the spaced primary gears land 2 integral with the couplet. Gear. couplet 50 is mounted onthe shaft 23` adjacent couplet 40 and includes the spaced primary gears 3 and 4. Gear couplet Sr-is mounted on shaft 23llocated adjacent couplet vand between that couplet and the adjacent right hand end'of the. shaft. The gear couplet 69 includes the spaced primary gears 5 and 6. Gear lof coupletV d: hasv the smallest diameterof any` one-of fthe gears ofi the series of couplet-gears and is located adjacent the left hand orpinner end of shaft 26; This gear I of couplet d provides for thelowest speed stepof the change speed mechanism, as will bevhereinaiterexplained, GearV 2 of'coupletl isA ofv increased diameter relative to the diametergo-fgear l and provides the` next-higher speed step of the change 'speedun-it C S; Gear-3 of couplet 5i) is ofgincreasedydiameter relative to the diameter-oi the adjacent-gear 2 of couplet 46, and ,each of the succeeding gears 4; Sand 6, is of increased diam- \eter relativel to the diameter-ofV the next-adjacent preceding gear respectively, of such seriesof primary gears, passing from left to right along shaft 23wl1en facing" Figs. 3A and-l; The gear 6 of couplet 59u provides for the highest speed; step of the Achange speed unit. Thus, primary gear couplets t0, 56 and 60 together provide a series of six (6) gears deninglsix (6) speed steps which provide for progressively increased rates ofspeed from the low speedstep dened by gear l of couplet 4,0 to the highY speed step dened by gear 6 of couplet 46i),-

The countergshaft 24. is positionedY above and extends acrossuunit QS, parallel witntheydriving Shaft. 23 0f' the. unit- Theseetionei theeounter shaft directly above driving shaft 23 providesthe driven shaft 25 forthe unit. Driven shaftsection 25 is provided with, the splines 25ml.tlflereerl.k

Three 3) secondary or driven drum gears, 19, Sil and 98 adeutedto be selectively driven from Ihe :primary gear eeuplets 4S. Seeed 60, respectively, are mounted and Splined. 0.11. driven YShaft 2 5 for rotating thesheit.4V These-drum gears are mounted.. and. Seeured en. Shaft 25i in, positions. ixedeeenst movements. ,axially of the-shaft- Drumsear lllis. ,mounted et the left handen@ ofV shaft 25 in position opposite andspaced above gear couplet 4.6 and includes the spaced spur gears 'H -andv'lZhconcentricwitlrthehshaft axis. Gear 'Il is of relatively large diameter compared" to gear I ofV primary couplet 45, while gear I2 has a smaller diameter than the diameter of the gear 1 I.

Drum gear 80 is mounted on driven shaft 25 adjacent and substantially abutting drum gear I in position lopposite and above primary gear couplet 50. Drum gear 80 includes the spaced spur gears 83 and 84 concentric with the axis of shaft 25, with gear 83 having a smaller diameter than the diameter of the adjacent gear 'I2 and gear 84 having a decreased diameter relative to the diameter of gear 83.

Drum gear 90 is mounted on driven shaft 25 adjacent and lsubstantially abutting drum gear 80 inv position above and opposite primary gear couplet 60. Drum gear 99 includes the spaced spur gears 95 and 96 thereon concentric with the axis of the driven shaft 25, with gear 95 being of smaller diameter than the diameter of the adjacent gear `84 of drum gear 80, and gear 96 being of smaller diameter than the diameter of the gear 95.

Thus, the spur gears of the secondary or driven drum gear units "I9, 89 and 90, progressively decrease in diameter from the rear end of driven shaft forwardly therealong to the forward end of that shaft, while the gears of primary gear couplets 40, 50, and 99, which are mounted on the driving shaft 23, progressively increase in inverse order relative to units 19, 89 and 9B, that is, progressively increase in diameter from the forward end. of shaft 23 rearwardly therealong to the rear end of that shaft.

The spacing of the pairs of gears, respectively, of the primary gear couplets 40, 50 and B0, and the diameters of these gears relative to the spacing and the diameters of the spur gears of the secondary gear units 1D, 8l) and 90, which are respectively opposite the primary gear couplets, is such that the gears I and 2 of couplet Ill extend between gears II and I2 of drum gear 15; the gears 3 and 4 of couplet 5I) extend between gears 83 and 84 of drum gear 8B; and the gears 5 and E of gear Icouplet 60 extend between gears 95 and 96 of drum gear 9D, when each of the gear couplets is in neutral or disengaged position relative to each ofthe drum gears respectively opposite and associated therewith.

Primary gear couplet 40 Ais movable axially on shaft 23 between a position with gear I thereof engaged with gear 'II of secondary gear unit 'I0 for the lowest speed step and a position with the gear 2 of the couplet engaged with gear 'I2 of gear unit 'I0 for the next highest speed step; primary gear couplet 59 is movable between position with gear 3 thereof engaged with gear 83 of secondary gear unit 80 for the third highest speed step and a position with gear 4 thereof engaged with gear 84 of unit 80 for the next highest speed step; and primary gear couplet 60 is movable between a position with gear 5 thereof engaged with gear 95 of secondary gear unit 99 for the fifth highest speed step and a position with gear 6 thereof engaged with gear 96 of unit 9U for the highest speed step of the six (6) speed steps of the change speed unit CS.

. Each of the primary gear couplets 4D, 50 and 6D, respectively, is movable to a neutral position, as. shown in Fig. 3, in which the gears of the coupletare disengaged from the gears of the respective secondary gear units 10, 80 or 90 to be driven thereby, so that, in such neutral position the primary gear couplet is completely disconnected from driving relation with its secondary or driven gear unit. Thus, by selective positioning of the gear couplets 40, 50 and 60, relative to the gear units 10, and 9D, the driving shaft 23 may be connected in driving relation with shaft n 25 for driving the shaft and the range gears L. I and H, on section 26 of that shaft, at any selected one of six (6) rates of speed defined and provided by gear sets I-'II, 2-l2, 3-83, '1 -8.4. 5-95 and 6--96, respectively.v Attention is here directed to the fact that in each of the selected speed steps for which change speed gear unit CS is adjusted, the engagement of only tWo (2) gears is required to drive counter shaft 24 and the range gears L, I and H on section 26 thereof, from the driving shaft 23 at the selected rate of speed. The primary or driving gear couplets 40, 50 and Si), and the secondary or driven gear units 10, til and 90, respectively, thus form gear trains of the simplest compound gear train form.

lIt is to be noted in connection with the above design and arrangement that the low speed primary gear couplet 49 is located on driving shaft 23 adjacent the rear end thereof and in immediate proximity to the rear bearing 23d of that shaft. Hence, when primary gear couplet 4I) is shifted rearwardly on shaft 23 to engage gears I and 1I for the lowest speed step of the unit, gear I engages with gear 1I in driving relation therewith at a location immediately adjacent the forward side of the rear bearing 23h. In this manner, lateral and` torsional deflections of shaft 23 under low speed step loads are maintained at a minimum.

Thus, in accordance with the invention, the change speed unit is formed of simple compound gear trains constituted by a set of two gears for each step, namely, a drivinggear and a driven gear, so that it is possible to attain for the secondary or driven gear of each set, a maximum diameter. With the secondary or driven gears of maximum diameter and, as in the example hereof, provided by gear units of drum form, preferably of solid material, having substantial width to provide the necessary spacing between the gears of each unit, the secondary gear units l0, 3E! and 90 on shaft 25, thus provide a total weight mass which Will develop a substantial fly-wheel effect acting on shaft 25.

As the sets of range gears L-SL; I-SI; and H--SI-I, are each contituted by the simplest compound gear train and have the driving gears L, I and H thereof directly driven from the driven shaft 25 of the change speed unit, it follows that a system of but two (2) shafts is required between the motor driven transmission and the cutter spindle 20, and further that any stepof the full range of steps, such as the eighteen (18) speed step range of this particular example, may be selectively set up by the use of but two (2) shifts, namely, a primary shift of the gear couplets 40, 59 and 65 on shaft 23 of the change speed unit, and a range shift of range gears S, I and H on the shaft 26. In this manner, any necessity for a secondary shift is eliminated.

A manually operable control is provided for selectively operating the change speed unit CS to set up any one of the six (6) speed steps at which counter shaft 24 may be driven from the driving shaft 23, such a control being more or less schematically illustrated in Fig. 4 of the drawings. In this example, the control includes a hand crank GI which is positioned at the exterior of the face or dial mounting plate D of change speed unit CS, being located onplate D in position below hand crank 39 of the speed range selector control (see Fig. l). Hand crank 4| isxed on` the outer'end'ofV a horizontally disposed shaft 41a Which extends into unit CS and which carries at its inner end a Worm 42. A barrelI cam 43 is mounted on a horizontally disposed sha-ft 43a extending above and across shaft Mafwith its axis perpendicular to the axis of the latter shaft. A worm gear 42a is provided on and around drum cam 43 intermediate the length thereof and' concentric with the axis of' shaft 43a. Worm 42 of shaft 4ta is meshed with worin gear 42a-at the underside thereof for rotating. shaft 43a by rotation of hand crank 4|. The barrel camilla is provided with a cam groove 44 formed therearound at the left hand side of worm gear 42d.` when facing Fig. 4, and with another cam groove 45 formed therearound to the right of the worm gear.

Shifter forks 40a, 50a and 60a are-provided in engagement with the'gear couplets 40, 5|! and 60;. respectively, for operation to selectivelyshift the gear couplets. Shifter fork 40a is operated by rotation of barrel cam 43 through a cam follower 40o engaged in cani groove 44, shifter fork 40a being mounted on a suitable Slide 40e for movement by followerlib invopposite directions along astraight line path parallel with the axis of driven shaft' 23; Shifter forks 50a and 60a are xed-on aslide h for movement with such slide as a unit in either direction along a straight line path parallel with the axis of the driven shaft 23. Slide 50o is actuated to move shifter forks @im and a in either direction along the straight line path to simultaneously shift the gear couplets and 60 in either direction on driven shaft 2-5k by a cam follower 5Go which is engaged in cam groove 4&3 of the barrel cam 43.

With the change speed gear unit CS set by the' speed selector control for drivingr shaft 25 in the low speed step, gear couplet 4i? is in position with the gear thereof engaged with gear 7| of the drum gear 1B, while the remaining gears 2, 3, 4, 5 andr of the gear couplets are all maintained in disengaged neutral position.

With the change speed unit set in the foregoing low speed. selection position, then by rotation offhandicranklli inthe proper direction, barrel cam 43 and cam groove 44 thereof are rotated to cause movement of shifter fork 4ta to shift gear couplet liil'inra direction to disengage gear I thereof, and to engage gear 2 with gear 12 ofdrum gear to thus select and setup the next highest speed stop. During such movement of carrelcam 43, cam groove 45 thereof maintains gear couplets 5tv and 5|) in neutral disengaged positions.

Continued rotation of hand crank 4| in the same direction will rotate cam 43 to cause cam groove thereof to effect shifting of gear couplet 4UY to neutral position completely disengaged from drum cam "it, while cam groove 45 of cam 43 will thereafter become eifective'and cause movement of shifter Vfork: 5ta to shift gear couplet ifto engage gear 3` thereof. with the gear 83 of drum gear 8% tothus select and set up the next highest' speedv step; In this selection position, couplet Se' is maintainedin neutral, disengaged position'.

With the change speed gear unit set for the speedstep provided by the engagement'of gears S'and' 83, continued rotation of hand crank 4| in th'esame" direction will rotate the barrel cani 4'3`rtof cause" the cam-groove 45 thereof to move shifterrforks 5ta and 60a in synchronism to shift gear couplets 50 andV 60 so as to successively engage' theA sets of'gears 4 and 84, gears 5' aiid,

16 and gears 6 and 96, respectively, to thereby suc'-v cessively set up the respective steps' defined and provided by such sets of gears when engaged;

With hand' crank 4| in the selection position with the set of gears 6 and S6 in engagement to provide the highest speed stepY of the change speed unit, rotation of hand crank 4| in the reverse direction, that is, to the left or counterclock-Wise, will through the medium of the cam grooves 44 and 45, cause progressive movements of the shifter forks 60a, 50a and 40a, respectively, to successively shift gear couplets 60, 50 and 4! so as to progressively engage the Sets of gears 5 and-95, 4 and 84, and 3 and 83, 2 and T2, and I andY 'I-I, to thus successively set up the speed steps definedA and provided by each of said sets of gears'when engaged. From any selectionv position between the lowest speed step and the high est speed-step, the hand crank 4| 'may be rotated in either direction to a desired speed selection position so as to cause the shifter mechanism to engage and set up the set of gears for the selected speed step.

The design and construction of the change speed unit CS with its selectively shiftable driving gear couplets 4i),k 5i) and B and gear units '10, 36 and 9|) selectively driven therefromfor driving the counter shaft 24 and its range gears L, I and H, is such that the enga-gement of only two (2) gears of the change speed unit CS is required for each speed step selected and set up.

A speed step selector dial DS is mounted on the exterior of dial plate D on the outerend of stub shaft 4t positioned above and parallel With hand crank actuated shaft 4|a. The inner end of stub shaft 4E mounts a relatively large diameter spur gear 46a which is engaged With and driven by a pinion lllb mounted on hand crank rotated shaft 41a. Hence, rotation of shaft 4Ia causes rotation of gear 46a to rotate stub shaft 46 and the speed step selector dial DS. The face of the speed step selection dial DS may be formed to provide three (3) concentric speed bands thereon, one for each basic speed range, and the face of the dial is further dividedinto six (6) sectors, oneffor each speed step provided by the change speed gear unit CS. The portion of each speed band in each sector is provided with a numeral indicating one of the eighteen (18) speed steps of the overall speed range provided by the drive of the example, as generally illustrated in Fig. 1. The gear ratio between pinion 4| b on speed selector shaft 4|a and the'dial plate gear 46a is'such'that rotation of hand crank 4| to a selection position for any one of the six (6) speed steps of the change speed unit CS will rotate the dial DS to position the sector which bears the speed indicia for that step. at the index or reading point provided for the dial.

In operation of the change speed spindle of the invention in the'particula'r form thereof here presented, the operator through the medium of the speed range selection crank 3S, engages and sets up either one of the sets of range gears L-SL, I-SI, or H-SH, for either the low, intermediate or high speed range, respectively, and

then by operation of the speed step selector haod crank 4|, sets up the desired one (1) of the six (6) speed steps of the change speed unit CS at Which it'is desired toV drive spindle 2S within'the selectedY basic speed range. Thus, the drive'of the example provides for eighteen (18) speed steps" in the' overall speed range within which spindle 2t maybe driven. Each speed step selected and set up frolnthesixV (6) available speed steps of the change speed unit CS is effected by the engagement of only two (2) gears of the unit for rotating counter shaft 2li from driving vshaft 23 at the rate of speed determined by that step. And as each basic speed range selected and set up from the three (3) available basic speed ranges lprovided by the three (3) sets of range gears is .going arrangement it is possible to utilize only two (2)V lines of shafting, namely, 22-23 and 24 (25-26) between the power driven pulley SP and the cutter spindle 26. Further by the mounting and arrangement of such two (2) lines of shafting and of the change speed unit CS associated therewith, relative to the power pulley SP, located at the rear of the column structure it and to the nose 2l of spindle 2d, located at the forward side of such column structure, it is possible to mount at least three (3) range gears, such as the range gears SH, SI, and SL, directly on the cutter spindle in immediate proximity to the nose 2| of that spindle, and all enclosed and housed within the available space provided by the normal dimensions and shape of the column structure ill.

While in the mechanical expression of a drive embodying my invention adapted to the particular horizontal spindle milling machine of the selected example, I have disclosed a drive providing for three (3) basic speed ranges with three (3) of the range gears of the sets of gears for such ranges directly mounted on the cutter spindle, it is contemplated and included within the scope of my invention to provide a drive for four (4) or more basic speed ranges embodying the direct mounting on the cutter spindle of four (4) or more range gears. In such a drive of the invention providing for more than three (3) basic speed ranges and the mounting of the requisite number of range gears directly on the cutter spindle, such spindle will be driven in accordance with that important feature of my invention by but two (2) active gear contacts between the power drive and the cutter spindle. And similarly, irrespective of whether three (3) or more basic speed ranges are provided, the change speed gear unit may provide for a greater or lesser number of speed steps than the six (6) speed steps provided by the unit CS of this example. As to those features of the invention by which range gears are directly mounted on the spindle in immediate proximity to the nose of the spindle and by which such gears are formed to provide a heavy weight mass for ily wheel effect at the nose end of the spindle, my invention is not limited to the use thereof with a drive which provides three (3) or more spindle mounted range gears but is applicable to a drive having less than three range gears. It should also be noted that the feature of a drive of my invention which provides driving a cutter spindle from a power drive by solely two (2) active gear contacts between that drive and the spindle is intended to be of general adaptability and is not restricted to use in a drive having three (3) or more spindle mounted range gears.

It will also be evident that various other embodiments, mechanical expressions, construc- Vi8 tions, combinations, and subcombinations may be resorted to without departing from the broad spirit and scope of my invention, and hence, I do not desire to limit and restrict my invention in all respects to the specific disclosures hereof as illustrated and described herein by way of example, except as may be required by specific intended limitation thereto in any of the appended claims.

What I claim is:

l. In combination, a rotary cutter spindle having an operating nose at one end thereof; a driven shaft opposite and parallel with that portion of said spindle immediately adjacent the operating nose thereof; sets of pairs of range gears defining high, intermediate and low speed ranges, re-

spectively; said high speed set comprising a gear directly mounted on said spindle at the inner end of the spindle nose in immediate proximity thereto, and a gear mounted on said driven shaft; said intermediate speed set comprising a gear mounted directly on said spindle in immediate juxtaposition with the inner side 'of said spindle mounted high speed gear, and a gear mounted on said driven shaft; said low speed set comprising a gear mounted on said spindle of a large diameter relative to the diameters of said intermediate and high speed spindle mounted gears and being positioned in immediate juxtaposition with the inner side of the spindle mounted intermediate gear, and a pinion gear mounted on said driven shaft having a small diameter relative to said spindle mounted low speed gear; and said spindle mounted intermediate and low speed gears being each formed with an `axially extended relatively wide, solid material hub portion adapted to provide a large weight mass in immediate proximity to the nose end of said spindle.

2. In combination, a rotary cutter spindle having at one end thereof an operating nose; a series of at least three (3) range gears mounted directly on said spindle; the outermost of said gears be- I ing mounted at the inner end of said operating nose in driving connection with said spindle; the intermediate of said gears being mounted on said spindle in driving connection therewith at the inner side of and in juxtaposition with said outermost gear; the innermost of said gears being mounted on but unconnected directly with said spindle in position thereon at the inner side of and in juxtaposition with said intermediate gear; and said innermost gear being directly connected at the forward side thereof in driving connection with said intermediate gear.

3. In combination, a rotary cutter spindle having an operating nose at one end thereof; a series of at least three (3) range gears mounted on said spindle; the outermost of said gears being connected directly with said spindle and being positioned thereon at the inner end of said operating nose; the intermediate of said gears being directly connected with said spindle in position thereon at the inner side of and in juxtaposition with said outermost gear; said intermediate gear having a relatively large diameter solid material hub portion extended inwardly therefrom on said spindle; the innermost of said gears being unconnected directly with said spindle and being mounted thereon in position at the inner side thereof in juxtaposition with said intermediate gear; said innermost gear having a relatively large diameter solid material hub portion extended forwardly therefrom to said inwardly extended hub portion of said intermediate gear; and the hub portion of said innermost gear be- 19 ing directly connected With the hub portion of said intermediate gear.

4. In combination, a rotary cutter spindle having an operating nose at one end thereof; a series of at least three (3) range gears mounted on said spindle; the outermost of said gears being directly connected with said spindle and being mounted. thereon in position at the inner side of said nose; said outermost gear being of relatively small diameter and substantial width and having a solid material hub portion; the intermediate of said gears being of greater diameter than said outermost gear and being directly connected with said spindle in position thereon at the inner side of and in juxtaposition with said outermost gear; said intermediate gear being provided with a relatively large diameter solid material hub portion extended inwardly therefrom; the innermost of said gears being of greater diameter than said intermediate gear and being unconnected directly with said spindle in position thereon at the inner side of and in juxtaposition with said intermediate gear; said innermost gear being provided with a relatively large diameter solid ma- 20 terial hub portion extended forwardly therefrom to the inner side of the hub portion of said intermediate gear; and the forward side of the hub portion of said innermost gear being directly connected with the hub portion of said intermediate gear.

THEODORE F. ESERKALN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,145,236 Fay July 6, 1915 1,233,500 Parsons July 17, 1917 1,416,285 Griiiin May 16, 1922 1,490,894 Einstein Apr. 15, 1924 2,115,058 Armitage Apr. 26, 1938 2,192,856 Henninger Mar. 5, 1940 2,239,567 Henninger Apr. 22, 1941 2,303,270 Grover Nov. 24, 1942 2,355,869 Johnson Aug. 15, 1944 2,430,127 Kronenberg et al. Nov. 4, 1947 

